US4145089A - Vehicle load-controlled brake pressure regulating valve device - Google Patents

Vehicle load-controlled brake pressure regulating valve device Download PDF

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Publication number
US4145089A
US4145089A US05/839,703 US83970377A US4145089A US 4145089 A US4145089 A US 4145089A US 83970377 A US83970377 A US 83970377A US 4145089 A US4145089 A US 4145089A
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US
United States
Prior art keywords
valve
piston
control
fluid pressure
pressure
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US05/839,703
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English (en)
Inventor
Erich Reinecke
Helmut Ulrich
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Wabco Westinghouse GmbH Germany
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Wabco Westinghouse GmbH Germany
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/18—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to vehicle weight or load, e.g. load distribution
    • B60T8/1812—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to vehicle weight or load, e.g. load distribution characterised by the means for pressure reduction
    • B60T8/1825—Means for changing the diaphragm area submitted to pressure

Definitions

  • the present invention relates to a load-controlled fluid pressure regulating valve device for tractor-trailer type vehicle brake systems.
  • the brake system should be provided with means for obtaining an emergency brake application in the event of a break in the supply line.
  • the object of the invention is to provide an economical valve device having a unitary valve construction by means of which the vehicle brake pressure is controlled in the fashion of a relay valve load regulating valve and emergency valve.
  • a valve device which, by reason of its unitary piston valve assemblage, converts the brake control pressure, which is usually provided by a regulating valve device and supplied to a relay valve device into direct movement of the piston valve assemblage the position of which is adjusted according to the vehicle load condition.
  • the piston valve assemblage directly actuates the supply valve via which fluid pressure from the supply reservoir is admitted to the brake cylinders.
  • an emergency actuating piston whose movement, upon loss of the air tank supply pressure between the tractor and trailer, is transmitted via the piston valve assemblage to directly actuate the supply valve.
  • FIG. 1 is a sectional view of a preferred form of the load-controlled brake power regulating valve device according to the invention.
  • FIG. 2 is a partially sectionalized view of the brake power regulating valve device shown in FIG. 1 and as viewed from the left thereof in the direction indicated by the arrows II.
  • FIGS. 3, 4 and 5 are diagrams in graphic form, showing the relationship between pressure and time in the control process, FIG. 3 showing the ratio when using only one brake pressure control valve, FIG. 4 showing the ratio when using a brake pressure control valve and, in addition, a relay valve, and FIG. 5 showing the ratio when using the brake pressure regulating valve device embodying the invention.
  • a self-lapping type piston valve assemblage comprising a relay piston 2 and actuable by a control piston diaphragm secured at its outer periphery in housing 1.
  • Piston 2 has coaxially operably disposed therein a valve member 5 which is biased downwardly, as viewed in the drawing, by a spring 4.
  • Valve member 5 cooperates with a supply valve seat 6 formed on the inner wall of piston 2 and with an exhaust valve seat 7 surrounding the upper end of a hollow piston rod 8 axially aligned underneath valve member 5.
  • Valve member 5 therefore, cooperates with supply valve seat 6 and exhaust valve seat 7 to function as both a supply and exhaust valve.
  • the piston 2 is provided with a plurality of radially outwardly extending fins 9 the lower surfaces of which are tapered to form a conically-shaped surface in juxtaposed relation with diaphragm 3.
  • Housing section 1 is provided with a corresponding number of radially inwardly extending fixed fins 10 which are so positioned and spaced as to fit within the interspaces of fins 9 without making contact therewith, said fins 10 also having lower surfaces which form a cone-shaped contour tapered oppositely to that formed by said fins 9 and making contact with diaphragm 3, as shown in FIG. 1.
  • Diaphragm 3 as above noted is secured at its outer periphery in the housing section 1 and is secured at its inner periphery to piston 2, said piston and diaphragm thus forming the control piston valve assemblage above mentioned.
  • Relay piston 2 has an upper pressure area 11 of fixed dimension and forming part of a control chamber 12 which is located above the relay piston 2 and communicates with a fluid pressure control passageway 13 via which said chamber is communicated with the motor vehicle brake valve shown symbollically.
  • the brake valve is located on the tractor portion of vehicle and connects air from the tractor air supply tank to the tractor brakes and to the trailer control valve device of the present invention, by appropriate piping, as shown.
  • the under side of diaphragm 3 comprises pressure area 14 which partially defines a delivery chamber 15.
  • Chamber 15 communicates with a delivery passageway or outlet 16 via which said chamber is communicated with brake cylinders shown symbollically. Chamber 15 is further communicable, when valve member 5 is in an unseated or open position relative to supply valve seat 6 via a supply chamber 17a, with a fluid pressure supply inlet 17.
  • a pilot pressure valve assemblage which comprises a pilot valve member 18 having a fluted stem, and a pilot diaphragm 19 operably connected therewith, is disposed in such a manner that, when said pilot valve member is in an unseated or open position relative to a pilot valve seat 20 fixed in the housing, a fluid pressure connection is established, via a chamber 21 and a passageway 22, between a control chamber 23, located above the diaphragm 3 (and in which fins 11 and 12 are located), and chamber 12.
  • a spring 24 compressibly disposed between the housing section 1 and diaphragm 19 is adjustable by means of a screw 25 so as to set the pilot pressure.
  • a coaxial bore 26 in housing section 1 coaxially slidably accommodates the hollow rod 8 whose upper open end, as already mentioned, forms the exhaust valve seat 7.
  • exhaust valve seat 7 occupies an unseated or exhaust position relative to valve member 5
  • fluid pressure may be vented via a coaxial passageway 27 in rod 8 and a vent port 28.
  • the rod 8 is operably engaged by a cam member 29, whose position is determined by vehicle weight or axle load.
  • a shaft or load lever 30 with a lever 31 secured thereto provides an operating connection between cam 29 and the vehicle axle (not shown).
  • Lever 31 in conventional manner, translates the degree of vehicle spring deflection, as determined by the vehicle load, through shaft 30 to cam 29. If more practical, a metal bellows (not shown) could be employed for translating vehicle spring deflection.
  • actuating brake pressure as delivered by the motor vehicle brake valve is also communicated to control chamber 12 via passageway 13 and flows via passageway 22, past the normally open or unseated valve 18, and via a passageway 22a to the upper face of diaphragm 3.
  • control pressure thus acting on the upper face of the diaphragm 3 effects either a reduction or an increase in control pressure in the case of low brake pressure supplied to the subsequent control valve devices and brake cylinders of the system in accordance with the load.
  • valve member 5 occupies a seated position on both valve seats 6 and 7, or a lapped position in which the pressure now prevailing in the brake cylinders corresponds to the pressure as controlled in accordance with the weight of the load.
  • the pressure which can then be measured in the brake cylinders when the vehicle is fully loaded corresponds to the pressure supplied to the brake power regulator from the motor vehicle brake valve which is at a 1:1 ratio.
  • the pressure supplied to the brake power regulator from the motor vehicle brake valve which is at a 1:1 ratio corresponds to the pressure supplied to the brake power regulator from the motor vehicle brake valve which is at a 1:1 ratio.
  • brake pressure has been reduced, fluid pressure present in the brake cylinders causes the piston 2 to move to its final, upper or release position, said pressure being vented to atmosphere past unseated valve member 5 and via bore 27 in the rod 8 and vent port 28.
  • Brake valve housing 1 is provided in its upper area with a housing section 40 separated from housing section 1 by a wall 48. Contained within housing section 40 is an emergency brake piston 41 having a rod 42 which is guidably sealed in a bore 40a in wall 48 and is engageable with the face 11 of piston 2. Fluid pressure in the fluid pressure supply line extending between the tractor and the trailer is admitted via a port connection 44 in housing section 40 to a chamber 43 formed under piston 41.
  • a one-way check valve in the form of an annular lip seal 46 formed by a packing cup that surrounds the periphery of piston 41 conducts the flow of fluid pressure past the piston to a chamber 45 above piston 41, while preventing backflow of fluid pressure from chamber 45 to chamber 43.
  • a passageway 49 (FIG.
  • chamber 45 connects chamber 45 to an air supply tank via the supply inlet connection 17.
  • the supply fluid pressure for the trailer brakes is thus stored in this supply tank.
  • a spring 47 is disposed in chamber 45 so as to urge piston 41 upwardly to its normal position, shown, in which a rod end 42 of piston 41 is disengaged from piston 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Hydraulic Control Valves For Brake Systems (AREA)
  • Regulating Braking Force (AREA)
US05/839,703 1976-10-14 1977-10-05 Vehicle load-controlled brake pressure regulating valve device Expired - Lifetime US4145089A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2646288A DE2646288B2 (de) 1976-10-14 1976-10-14 Lastabhängige Bremskraft-Regeleinrichtung
DE2646288 1976-10-14

Publications (1)

Publication Number Publication Date
US4145089A true US4145089A (en) 1979-03-20

Family

ID=5990394

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/839,703 Expired - Lifetime US4145089A (en) 1976-10-14 1977-10-05 Vehicle load-controlled brake pressure regulating valve device

Country Status (14)

Country Link
US (1) US4145089A (de)
JP (1) JPS5349675A (de)
AT (1) AT365522B (de)
BE (1) BE859715A (de)
CH (1) CH625469A5 (de)
DE (1) DE2646288B2 (de)
ES (1) ES463153A1 (de)
GB (1) GB1588039A (de)
IT (1) IT1116338B (de)
NL (1) NL7710858A (de)
PL (1) PL112557B1 (de)
SE (1) SE435360B (de)
SU (1) SU725550A1 (de)
YU (1) YU39190B (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4421360A (en) * 1981-01-14 1983-12-20 General Signal Corporation Relay valve assembly
US4438980A (en) * 1981-03-27 1984-03-27 Bendix Limited Proportioning valve with pressure port communicating with stepped area of differential piston
US4597610A (en) * 1979-09-25 1986-07-01 Robert Bosch Gmbh Load-dependent brake force governor
US5662391A (en) * 1996-01-16 1997-09-02 Westinghouse Air Brake Company Pneumatic empty/load proportioning for electro-pneumatic brake
US20100001578A1 (en) * 2006-09-15 2010-01-07 Siemens Aktiegesellschaft Hydraulic Brake Comprising a Safety Function

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2706758A1 (de) * 1977-02-17 1978-08-24 Wabco Westinghouse Gmbh Bremskraftregeleinrichtung fuer anhaengerbremsanlagen mit einem notbremsventil
DE3026252C2 (de) * 1980-07-11 1983-12-08 Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover Lastabhängig gesteuerte Bremskraft-Regeleinrichtung
EP0049114B1 (de) * 1980-10-01 1986-02-05 Bendix Limited Ventil mit veränderlichem Druckverhältnis
DE3041248A1 (de) * 1980-11-03 1982-06-09 Wabco Fahrzeugbremsen Gmbh, 3000 Hannover Vorrichtung zum justieren eines mechanisch gesteuerten lastabhaengigen bremskraftreglers
DE3639149C2 (de) * 1986-11-15 1998-03-26 Wabco Gmbh Lastabhängig steuerbare Bremskraftregeleinrichtung
DE102022115721A1 (de) 2022-06-23 2023-12-28 Bayerische Motoren Werke Aktiengesellschaft Verfahren und Regeleinrichtung für eine automatische Bremsregelung eines Kraftfahrzeugs

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3302982A (en) * 1965-04-30 1967-02-07 Westinghouse Bremsen Apparate Load-dependent empty-load valve
US3945689A (en) * 1973-11-28 1976-03-23 Jidosha Kiki Co., Ltd. Combined load-sensing proportion and relay valve

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1922866U (de) * 1963-09-12 1965-09-02 Bosch Gmbh Robert Druckmittelbremsvorrichtung.
DE1505533A1 (de) * 1966-01-26 1969-10-23 Bosch Gmbh Robert Steuerventil,insbesondere fuer Kraftfahrzeuganhaengerbremsen
DE1977311U (de) * 1967-09-26 1968-01-18 Werner Schilling Anhaenger-steuerventil mit bremskraftregler fuer eine druckluftbetriebene fahrzeug-bremsanlage.
DE1630189C3 (de) * 1967-11-09 1975-04-17 Robert Bosch Gmbh, 7000 Stuttgart Lastabhängig einstellbares Bremsventil für Druckluftbremsanlagen von Fahrzeuganhängern
DE1958808B2 (de) * 1969-11-22 1973-11-29 Westinghouse Bremsen- Und Apparatebau Gmbh, 3000 Hannover Relaisventil zur Verwendung als Anhängerbremsventil fur Zweikreis Druckluftbremsanlagen von Straßen fahrzeugen
DE2004227B2 (de) * 1970-01-30 1973-05-24 Knorr Bremse GmbH, 8000 München Membrankolben

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3302982A (en) * 1965-04-30 1967-02-07 Westinghouse Bremsen Apparate Load-dependent empty-load valve
US3945689A (en) * 1973-11-28 1976-03-23 Jidosha Kiki Co., Ltd. Combined load-sensing proportion and relay valve

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4597610A (en) * 1979-09-25 1986-07-01 Robert Bosch Gmbh Load-dependent brake force governor
US4421360A (en) * 1981-01-14 1983-12-20 General Signal Corporation Relay valve assembly
US4438980A (en) * 1981-03-27 1984-03-27 Bendix Limited Proportioning valve with pressure port communicating with stepped area of differential piston
US5662391A (en) * 1996-01-16 1997-09-02 Westinghouse Air Brake Company Pneumatic empty/load proportioning for electro-pneumatic brake
AU707178B2 (en) * 1996-01-16 1999-07-01 Westinghouse Air Brake Company Pneumatic empty/load proportioning for electro-pneumatic brake
US20100001578A1 (en) * 2006-09-15 2010-01-07 Siemens Aktiegesellschaft Hydraulic Brake Comprising a Safety Function
AU2007296840B2 (en) * 2006-09-15 2012-02-23 Siemens Aktiengesellschaft Hydraulic brake
CN101511654B (zh) * 2006-09-15 2013-01-23 西门子公司 具有安全功能的液压制动装置
US8915553B2 (en) * 2006-09-15 2014-12-23 Siemens Aktiengesellschaft Hydraulic brake comprising a safety function

Also Published As

Publication number Publication date
IT1116338B (it) 1986-02-10
CH625469A5 (de) 1981-09-30
ES463153A1 (es) 1978-07-16
PL112557B1 (en) 1980-10-31
SU725550A3 (en) 1980-03-30
BE859715A (fr) 1978-02-01
ATA593877A (de) 1981-06-15
NL7710858A (nl) 1978-04-18
SE7710438L (sv) 1978-04-15
YU244877A (en) 1982-06-30
AT365522B (de) 1982-01-25
JPS5349675A (en) 1978-05-06
SU725550A1 (ru) 1980-03-30
DE2646288A1 (de) 1978-08-31
GB1588039A (en) 1981-04-15
SE435360B (sv) 1984-09-24
YU39190B (en) 1984-08-31
PL201436A1 (pl) 1978-04-24
DE2646288B2 (de) 1979-09-27

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